US3194581A - Anti-roll devices for automobile vehicles - Google Patents

Anti-roll devices for automobile vehicles Download PDF

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Publication number
US3194581A
US3194581A US265273A US26527363A US3194581A US 3194581 A US3194581 A US 3194581A US 265273 A US265273 A US 265273A US 26527363 A US26527363 A US 26527363A US 3194581 A US3194581 A US 3194581A
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Prior art keywords
distributor
pressure
vehicle
fluid
vehicle body
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Expired - Lifetime
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US265273A
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English (en)
Inventor
Brueder Antoine
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Automobiles Citroen SA
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Andre Citroen SA
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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60G—VEHICLE SUSPENSION ARRANGEMENTS
    • B60G21/00—Interconnection systems for two or more resiliently-suspended wheels, e.g. for stabilising a vehicle body with respect to acceleration, deceleration or centrifugal forces
    • B60G21/10—Interconnection systems for two or more resiliently-suspended wheels, e.g. for stabilising a vehicle body with respect to acceleration, deceleration or centrifugal forces not permanently interconnected, e.g. operative only on acceleration, only on deceleration or only at off-straight position of steering
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60G—VEHICLE SUSPENSION ARRANGEMENTS
    • B60G21/00—Interconnection systems for two or more resiliently-suspended wheels, e.g. for stabilising a vehicle body with respect to acceleration, deceleration or centrifugal forces
    • B60G21/02—Interconnection systems for two or more resiliently-suspended wheels, e.g. for stabilising a vehicle body with respect to acceleration, deceleration or centrifugal forces permanently interconnected
    • B60G21/04—Interconnection systems for two or more resiliently-suspended wheels, e.g. for stabilising a vehicle body with respect to acceleration, deceleration or centrifugal forces permanently interconnected mechanically
    • B60G21/05—Interconnection systems for two or more resiliently-suspended wheels, e.g. for stabilising a vehicle body with respect to acceleration, deceleration or centrifugal forces permanently interconnected mechanically between wheels on the same axle but on different sides of the vehicle, i.e. the left and right wheel suspensions being interconnected
    • B60G21/055—Stabiliser bars
    • B60G21/0551—Mounting means therefor
    • B60G21/0553—Mounting means therefor adjustable
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60G—VEHICLE SUSPENSION ARRANGEMENTS
    • B60G21/00—Interconnection systems for two or more resiliently-suspended wheels, e.g. for stabilising a vehicle body with respect to acceleration, deceleration or centrifugal forces
    • B60G21/02—Interconnection systems for two or more resiliently-suspended wheels, e.g. for stabilising a vehicle body with respect to acceleration, deceleration or centrifugal forces permanently interconnected
    • B60G21/06—Interconnection systems for two or more resiliently-suspended wheels, e.g. for stabilising a vehicle body with respect to acceleration, deceleration or centrifugal forces permanently interconnected fluid
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10S280/00—Land vehicles
    • Y10S280/01—Load responsive, leveling of vehicle

Definitions

  • This invention relates to an anti-roll suspension device for automobile vehicles which is designed primarily for counteracting the action of centrifugal force on the vehicle body when cornering to permit the inclination of the vehicle body on the near wheels as desirableinstead of on the outer wheels, as usual.
  • the anti-roll device should become operative before the centrifugal force is created, and, preferably, its action antagonistic to the centrifugal force should cease before this force has dropped completely to zero.
  • the vehicle body must lean inwardly of the turn being negotiated, but this inclination should be limited to preserve a sufiicient possibility of wheel beat with respect to the suspension system. There is not inconvenience in predetermining this inclination so that it remains invariable irrespective of the radius of curvature of the bend and the velocity of the vehicle.
  • the speed at which the vehicle body is set in an inclined position should be a function of the rate at which the radius of curvature changes along the path followed by the vehicle.
  • this device comprising, in the vehicle suspension system, pressure-fluid receiving members for correcting the trim of the vehicle and a distributor connected to said member and responsive to the steering control in order selectively to distribute fluid under pressure to said receiving members according to the direction in which the control action is exerted on the steering wheel, with a view to produce a transverse inclination of the vehicle body on the side corresponding to the direction in which the steering wheel has been turned.
  • the aforesaid distributor is responsive to an auxiliary distributing device controlled by means responsive in turn to the transverse inclination of the vehicle body and adapted to discontinue the delivery of fluid under pressure to said distributor when a predetermined degree of inclination of the vehicle body has been attained.
  • this device is responsive to the direction in which the steering is actuated meets more particularly the first requirement set forth hereinabove, in that there is always a certain time lag between the moment the driver exerts the steering effort and the moment the vehicle is actually subjected to the centrifugal force.
  • the third requirement is obviously met provided that the variation in the cross-sectional passage area available for the pressure fluid delivered by the distributor is consistent with the quickness with which the driver actuates the steering control governing this distributor.
  • the direction in which the steering control effort is applied and even the magnitude of this effort can be sensed in various manners, but a particularly convenient method of sensing these parameters consists in utilizing the pressure values occurring in a servo-action steering control device, notably the values of the specific pressures built up in the chambers of the servo-assisted steering control mechanism; in this case, the distributor is responsive to these pressure values.
  • the aforesaid receiving members consist of hydraulic cylinders interposed, on at least one side of the vehicle, between the elements carrying the road wheels of the vehicle and the lever arms of front and rear torsion bars mounted in the fashion of stabilizing bars.
  • pressure-fluid receiving members designates as well any elements forming part of an existing suspension system, whether in the form of correcting hydraulic cylinders or pneumatic members acting themselves as suspension members.
  • FIGURE 1 is a very diagrammatic view showing an assembly comprising the two trains of road wheels of an automobile vehicle equipped with a conventional springtype suspension system and provided with the anti-roll device of this invention;
  • FIGURE 2 is a diagrammatic View showing more particularly the anti-roll device with the details concerning .its hydraulic control system together with the manner in which it is associated with a rear train of road Wheels, as seen from the rear;
  • FIGURE 3 is a view similar to FlG. 1 but illustrating the two trains of road wheels of an automobile vehicle equipped with a hydropneumatic suspension system provided with the anti-roll of thisinvention;
  • FIGURE 4 is a view similar to FIG. 2, showing more particularly details of hydraulic control means for the anti-roll device together with the manner in which it is associated with a rear train of road wheels, as seen from the rear;
  • FIGURE 5 is a partial cross-sectional and elevational view of a stop member associated with a valve.
  • the vehicle partially shown in FIG. 1 comprises a front train of road wheels 1 and a rear train ofroad wheels 2, mounted on the outer or free ends of swinging'or carrier arms 3, 4 pivoted at 5 and 6 on the vehicle body shown only in diagrammatic form at 7, front and rear suspension springs 8, 9, respectively, being mounted between said arms and said vehicle body, as shown.
  • the front wheels 1 are controlled by a servo-action steering system of any suitable and known design, which has been illustrated just to the extent necessary for the proper understanding of the invention.
  • This servo steering comprises a hydraulic device of which the cylinder 11 is secured on the vehicle body, the rod 12 of piston 13 slidably mounted in said cylinder 11 emerging from the latter and having its outer end connected through a linkage 14 to the steering arms 15 of wheels 1. It further comprises a distributor unit shown diagrammatically at 16 and connected to a source of fluid under pressure through a pipe line 17 and to the reservoir 18 of the-hydraulic system through another pipe line 19. This unit 16.
  • controlled by means of the steering column carrying the steering wheel 21 is adapted, according to the direction in which the steering wheel 21 is rotated, to deliver fluid under pressure into either of chambers 22 or 23 of cylinder 11 through the relevant line 24 or 25 while connecting the other chamber to the exhaust, so that the hydraulic device 18 will transmit to the front wheels a movement setting them in the proper angular position as a function of the angular extent to which the steering wheel 21 has been rotated.
  • the source of fluid under pressure of the system consists of a pump 26 connected to the aforesaid reservoir 18 and having associated therewith as already known per se a pressure accumulator 27.
  • the anti-roll device designed for inclining the vehicle body inwards when negotiating a curve consists of front and rear transverse torsion bars 30, 31 respectively, which are mounted for free rotation on the vehicle frame structure in the fashion er stabilizing bars and have their end lever arms connectedto the front and rear wheel carrier arms 3, 4, respectively, through means comprising hydraulic-cylinder devices.
  • a front hydraulic device32 and a rear hydraulic device 33 are provided, bothof which being of the double-acting type and disposed on the same side of the vehicle, the connection between the torsion bars and the wheel carrier arms being simple through link 34, 35 on the other side of the vehicle;
  • the cylinders of the hydraulic devices 32, 33 are pivotally connected to the end arm of the relevant torsion bar 3 8, 31 and the piston rods of these cylinders are connected to the corresponding wheel carrier arm 3, 4.
  • the lower chambers 32 33 of these hydraulic cylinders communicate with each other through a pipe line 36, and their upper chambers 32 33 communicate with each other through another pipe line 37. The delivery of fluid under pressure to either of these chambers of cylinders 32, 33 will thus permit of tightening the torsion bars and therefore creating a torque reacting to the rolling torque developed by the centrifugal force when the vehicle is negotiating a turn.
  • This action is controlled through the medium of a distributor 40 responsive to the steering control, in this case under the control of the pressure developed in either of the two, chambers of the hydraulic device 10 of the servo steering system.
  • the distributor 40 (FIG. 2) comprises two slide valves 41, 42 normally connecting lines 43, 44 (connected respectively to the interconnecting lines 36, 37 of cylinders 32, 33) with a duct 45 connected in turn through a line 46 to the fluid reservoir 18. These slide valves are also adapted to connect the pipe lines 43, 44 with ducts 47,
  • slide valves 41, 42 are normally urged to the position shown in FIG. 2 by the antagonistic action of springs 49, 5t and spring-loaded push-rods 51, 52 co-acting with the relevant ends of slide valves 41, 42 through a rocking lever 53 pivoted therebetween in the distributor body.
  • these push-rods 51, 52 constitute hydraulically controlled pistons having their control chamber 54, 55 connected through pipe lines 56, 5'7 to the lines 24, 25 leading to the chambers of the hydraulic device 10 of the servo steering mechanism. It may be noted that adequate steps are taken in this example whereby, when one slide valve is actuated by the corresponding hydraulic push-rod, the connection between the cylinders.
  • the distributor 40 is responsive to a' device sensing the transverse inclination of the vehicle body for controlling the delivery of pressure fluid to this distributor.
  • the rocking lever 53 takes care of only operating a single valve at one time, either 41 or 42, and the corresponding valve of the pushers 51 or 52 upon which is applied the strongest pressure prevailing in the working chamber corresponding to the screw of the servo-direction.
  • This transverse inclination sensing device comprises an auxiliary distribution device constituted by a pilot distributor 6t) co-acting with a relay valve 61 comprising in turn a slide valve member 62 normally positioned to connect the inlet ducts 47 and 4d of distributor 43 with a pipe line 63 connected to the source of fluid under'pressure.
  • This slide valve member :52 is urged to its normal position shown in the drawing by antagonistic springs housed incontrol chambers 64, as disposed at either end of the slide valve and connected through pipe lines es, -57 to the pilot distributor 69.
  • the latter comprises a twin type slide valve 58 adapted, in the normal position shown in the drawing, toconnect the lines 66, v67 with the lines 69, 70 connected in turn to the reservoir 18, and to be moved either way from this position to a position in which one of the pipe lines 65 or 67 is connected to a line '71 connected to the source of fluid under pressure, while leaving the other line 66 or 67 connected with the reservoir 18, at least during the actuation of the slide valve 62 of the relay valve device which results from this distribution.
  • the displacements of the twin valve 68 are controlled mechanically.
  • This anti-roll device operates as follows:
  • the distributor unit 16 of the servo-steering system delivers fluid under pressure into chamber. 22 of steering cylinder 11) through arline 24, and even before the front road wheels have started their angular movement the fluid pressure thus available simultaneously in line 56 and chamber 54 actuates the push-rod 51 controlling the slide valve 41 of distributor 40.
  • the slide valve 41 actuated immediately causes the pressure-fluid inlet duct 47 to communicatewith the pipe line 43 leading to the line 36 interconnecting the. lower chambers of the hydraulic cylinders 32, 33 having their upper chambers connected to the exhaust.
  • twin slide valve 68 of pilot distributor 6t resumes its initial, intermediate position and allows the slide valve member of relay valve 61 to resume its inoperative position by restoring the connection between line 66 and line 69 connected with the fluid reservoir 18.
  • FIGS. 3 and 4 illustrate a typical application of the anti-roll device of this invention similar to the device described hereinabove to a vehicle equipped with a hydropneumatic suspension system of known design, wherein a hydraulic interconnection is provided between the suspension units of each train of wheels, this arrangement being broadly explained hereinafter:
  • the suspension units designated by the reference numerals 80 and $1 for the front and rear trains of wheels respectively consist each of a hollow sphere 82 divided by a flexible diaphragm 84 into an upper chamber 83 filled with gas acting as a suspension spring and a lower liquid-filled chamber bounded on the other hand by a piston 85 slidably fitted in a cylinder 86 at the bottom of the sphere 82, this cylinder being on the other hand secured on the vehicle body, the rod of piston 85 hearing on the relevant wheel carrier arm.
  • the cylinders of the front and rear suspension unit 80 and 81 respectively communicate through pipe lines 87, 88 connected each at 89 and 9%) to a pressure-fluid distributor (not shown) acting, as already known per se, as a device for correcting the vertical trim of the vehicle body.
  • FIGS. 3 and 4 of the drawings is on the other hand similar to that of FIGS. 1 and 2, except for the fact that the distributor 40 corresponding to distributor 40 of the first form of embodiment is controlled by complementary means, whereby all the elements of FIGS. 3 and 4 which are similar to those of FIGS. 1 and 2 are simply designated by the same reference numerals in FIGS. 3 and 4.
  • rocking lever 91 co-acting with said slide valves and pivoted at 92 in the distributor body, and comprising a control lever 83 connected through cable or rods 94, 95 to bell-crank levers 96, 97 pivoted at 98, 99 on the body of the vehicle and connected on the other hand to traction springs 100, 101 anchored at one point of the wheel carrier arms 4 which is spaced from their pivot axis.
  • the rocking lever 91 co-acts with said slide valves 41 42 by unidirectional engagement, so as to actuate only one of them at a time in the direction to change the pressure-fluid distribution, the outer ends of the arms of said rocking lever engaging notches 102, 103 formed in the slide valves, said arms being thus allowed a certain unidirectional free beat.
  • This trim correction control arrangement operates as follows:
  • the rocker lever 91 will actuate the slide valve 42 of distributor 49 and thus connect the pressure-fluid inlet duct 48 with the pipe line 44, that is, with the line 37 interconnecting the upper chambers of cylinders 32, 33 of which the lower chambers remain connected to the exhaust through the nonactuated slide valve 41
  • both hydraulic devices 32, 33 contract and app-1y to the wheel carrier arms through the torsion bars 30, 32 and links 34, 35 a torque tending to restore the vehicle body to its normal position, that is, to urge the pivot pin of the left-hand arm downwardly and the pivot pin of the right-hand arm upwardly.
  • the reverse correction is effected when the body tends to lean on the left-hand side.
  • Anti-roll device for an automobile vehicle having a suspension system comprising fluid-pressure receiving members to correct the trim of the vehicle, servo steering control means having a servo steering distributor and a servo steering control cylinder with two chambers connected to the latter, a pressure fluid distributor connected to said members and responsive to said servo steering control means to selectively distribute,'in response to the direction in which the steering wheel is actuated, fluid under pressure to said receiving members to cause the vehicle body to lean transversely on the side corresponding to the direction in which the steering wheel has been actuated, said distributor being actuated selectively by means of fluid under pressure from said servosteering control means, the selective control of said ressure fluid distributor being responsive to the pressures prevailing in said two chambers of the servo steering control cylinder, a transverse inclination sensing device comprising an auxiliary distributing device, said auxiliary distributing device cooperating with said pressure fluid distributor to discontinue the delivery of fluid under pressure to said distributor when a predetermined transverse inclination of the vehicle
  • Anti-roll device according to claim 1 wherein said receiving members comprise hydraulic cylinder devices interposed at one siderof the vehicle between the members carrying the road Wheels of the vehicle and the lever arms of the front and rear torsion bars mounted as stabilizing bars.
  • Anti-roll device according to claim 1, wherein said pressure fluid distributor is responsive to a complementary control device responsive to the transverse inclination of the vehicle body and monitoring the distribution of fluid under pressure to said receiving members in the direction tending to neutralize any transverse inclination of the vehicle body, said pressure fluid distributor having control means on which the action of said servo steering control means is preponderant'with respect to that of said complementary control device for selectively distributing fluid under pressure to said receiving members.
  • Anti-roll device according to' claim 1 wherein said pressure fluid distributor comprises two slide valves to carry out said selective distribution of fluid under pressure, a rocker interposed between said slide valves and responsive, for each slide valve, to a control push-rod, said push-rod being actuated through the medium of fluid under pressure from the servo steering distributor.
  • Anti-roll device comprises two slide valves for carrying out said selective pressure-fluid distributions, at pressure-fluid inlet duct for each of said slide valves, said auxiliary distribution device comprising a pilot distributor responsive to the control means sensing the vehicle body inclination, and a pressure-fluid control relay valve responsive to said pilot distributor to block either of said 'inlet ducts when the aforesaid predetermined inclination is attained.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Vehicle Body Suspensions (AREA)
US265273A 1962-03-15 1963-03-14 Anti-roll devices for automobile vehicles Expired - Lifetime US3194581A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
FR891242A FR1325058A (fr) 1962-03-15 1962-03-15 Dispositif anti-roulis pour véhicule automobile

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US3194581A true US3194581A (en) 1965-07-13

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US265273A Expired - Lifetime US3194581A (en) 1962-03-15 1963-03-14 Anti-roll devices for automobile vehicles

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US (1) US3194581A (de)
BE (1) BE628690A (de)
DE (1) DE1455943B1 (de)
ES (1) ES286039A1 (de)
FR (1) FR1325058A (de)
GB (1) GB1037312A (de)
LU (1) LU43314A1 (de)
NL (1) NL289745A (de)

Cited By (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3285623A (en) * 1964-09-08 1966-11-15 Daimler Benz Ag Anti-tilting system for vehicles
US3300232A (en) * 1959-10-31 1967-01-24 Daimler Benz Ag Curve stabilization of motor vehicles
US3396984A (en) * 1965-06-30 1968-08-13 Citroen Sa Andre Anti-roll devices for automatic vehicles
US3556542A (en) * 1967-06-19 1971-01-19 Ind Dev Co Establishments Trim-correcting arrangement for vehicles with hydropneumatic suspension
US3625539A (en) * 1968-08-20 1971-12-07 Rover Co Ltd Vehicle suspensions
US3704027A (en) * 1970-01-08 1972-11-28 Sanfrancisco Cayetano Roque La Suspension system for motor vehicles
US3778081A (en) * 1971-05-12 1973-12-11 Honda Motor Co Ltd Automatic control system to provide stability to a vehicle
US3885809A (en) * 1972-03-08 1975-05-27 Automotive Prod Co Ltd Vehicle suspension
GB2148217A (en) * 1983-10-07 1985-05-30 David Cathcart Gorman Vehicle suspension
US4629023A (en) * 1985-08-27 1986-12-16 Go Pro S.R.L. Motor vehicle, or `kart` with independent suspension on all four wheels, for off-highway use
FR2752202A1 (fr) * 1996-08-09 1998-02-13 Fichtel & Sachs Ag Agencement de stabilisateur pour vehicule
FR2786132A1 (fr) * 1998-11-25 2000-05-26 Renault Dispositif de liaison d'une barre anti-roulis a un organe mobile du train d'un vehicule automobile
US6299181B1 (en) * 2000-12-07 2001-10-09 Caterpillar S.A.R.L. Vehicle having steerable wheels
US20040036244A1 (en) * 2000-08-11 2004-02-26 Marcus Kotulla Hydraulic suspension system for a vehicle
US7806417B1 (en) * 2008-09-08 2010-10-05 Hwh Corporation Height averaging means for use with a motor vehicle suspension control system
US9517673B2 (en) * 2014-07-18 2016-12-13 GM Global Technology Operations LLC Vehicle and a suspension system for the vehicle
CN111051090A (zh) * 2017-06-14 2020-04-21 标致雪铁龙汽车股份有限公司 用于机动车辆车桥的具有受控联接装置的防侧倾设备

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5914367B2 (ja) * 1978-06-08 1984-04-04 本田技研工業株式会社 車輌の懸架装置
FR2557039A1 (fr) * 1983-12-27 1985-06-28 Didier Girard Procede et ensemble pour la compensation anticipee du deportement de la caisse d'un vehicule dans les virages
GB8609198D0 (en) * 1986-04-15 1986-05-21 Mumford M A Vehicle suspension system
GB2235168A (en) * 1989-08-24 1991-02-27 Gkn Technology Ltd A vehicle suspension system having an adjustable anti-roll bar
DE4423859A1 (de) * 1994-02-03 1995-08-10 Ernst Huber Fahrzeug mit Ausgleichsvorrichtung
AT518478B1 (de) * 2016-04-07 2018-11-15 Melecs Ews Gmbh Aktuator für aktive Fahrwerke von Kraftfahrzeugen

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US2802674A (en) * 1955-11-16 1957-08-13 Gen Motors Corp Roll control system for a motor vehicle

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DE1071503B (de) * 1959-12-17
DE745155C (de) * 1937-09-09 1944-02-28 Paul H Mueller Dr Ing Einrichtung an Fahrzeugen zur Gegenwirkung gegen die Neigung des Wagenkastens beim Kurvenfahren
DE1051658B (de) * 1952-11-04 1959-02-26 Julius Lindblom Einrichtung zur Erhoehung der Kurvenstabilitaet von Fahrzeugen
FR1096561A (fr) * 1953-12-21 1955-06-22 Citroen Sa Andre Dispositif antiroulis pour véhicules
DE965293C (de) * 1955-06-24 1957-06-06 Daimler Benz Ag Kraftfahrzeug mit einer Vorrichtung zur Kurvenstabilisierung
DE1041813B (de) * 1957-03-15 1958-10-23 Daimler Benz Ag Einrichtung zur Kurvenstabilisierung, insbesondere bei Kraftfahrzeugen
DE1172132B (de) * 1958-09-02 1964-06-11 Daimler Benz Ag Einrichtung zum Schraegstellen des Wagen-kastens von Fahrzeugen, insbesondere Kraft-fahrzeugen, beim Kurvenfahren
FR1254827A (fr) * 1959-06-30 1961-02-24 Fischer Georg Procédé et dispositif de stabilisation d'axes de manivelles à suspension pneumatique
FR1271895A (fr) * 1959-10-31 1961-09-15 Daimler Benz Ag Dispositif pour assurer la stabilisation dans les virages sur des voitures automobiles

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US2802674A (en) * 1955-11-16 1957-08-13 Gen Motors Corp Roll control system for a motor vehicle

Cited By (19)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3300232A (en) * 1959-10-31 1967-01-24 Daimler Benz Ag Curve stabilization of motor vehicles
US3285623A (en) * 1964-09-08 1966-11-15 Daimler Benz Ag Anti-tilting system for vehicles
US3396984A (en) * 1965-06-30 1968-08-13 Citroen Sa Andre Anti-roll devices for automatic vehicles
US3556542A (en) * 1967-06-19 1971-01-19 Ind Dev Co Establishments Trim-correcting arrangement for vehicles with hydropneumatic suspension
US3625539A (en) * 1968-08-20 1971-12-07 Rover Co Ltd Vehicle suspensions
US3704027A (en) * 1970-01-08 1972-11-28 Sanfrancisco Cayetano Roque La Suspension system for motor vehicles
US3778081A (en) * 1971-05-12 1973-12-11 Honda Motor Co Ltd Automatic control system to provide stability to a vehicle
US3885809A (en) * 1972-03-08 1975-05-27 Automotive Prod Co Ltd Vehicle suspension
GB2148217A (en) * 1983-10-07 1985-05-30 David Cathcart Gorman Vehicle suspension
US4629023A (en) * 1985-08-27 1986-12-16 Go Pro S.R.L. Motor vehicle, or `kart` with independent suspension on all four wheels, for off-highway use
FR2752202A1 (fr) * 1996-08-09 1998-02-13 Fichtel & Sachs Ag Agencement de stabilisateur pour vehicule
FR2786132A1 (fr) * 1998-11-25 2000-05-26 Renault Dispositif de liaison d'une barre anti-roulis a un organe mobile du train d'un vehicule automobile
US20040036244A1 (en) * 2000-08-11 2004-02-26 Marcus Kotulla Hydraulic suspension system for a vehicle
US7040631B2 (en) * 2000-08-11 2006-05-09 Kinetic Pty. Ltd. Hydraulic suspension system for a vehicle
US6299181B1 (en) * 2000-12-07 2001-10-09 Caterpillar S.A.R.L. Vehicle having steerable wheels
US7806417B1 (en) * 2008-09-08 2010-10-05 Hwh Corporation Height averaging means for use with a motor vehicle suspension control system
US9517673B2 (en) * 2014-07-18 2016-12-13 GM Global Technology Operations LLC Vehicle and a suspension system for the vehicle
CN111051090A (zh) * 2017-06-14 2020-04-21 标致雪铁龙汽车股份有限公司 用于机动车辆车桥的具有受控联接装置的防侧倾设备
CN111051090B (zh) * 2017-06-14 2023-03-10 标致雪铁龙汽车股份有限公司 用于机动车辆车桥的具有受控联接装置的防侧倾设备

Also Published As

Publication number Publication date
LU43314A1 (de) 1963-05-07
BE628690A (de)
ES286039A1 (es) 1963-05-01
GB1037312A (en) 1966-07-27
NL289745A (de)
FR1325058A (fr) 1963-04-26
DE1455943B1 (de) 1970-03-12

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